Cam feeder and die

ABSTRACT

In a feeder die system, a gag system is provided which is adapted to simultaneously operate a plurality of actuators permitting reciptocating movement of feeder bar of a die. Provision is further made for utilizing the actuating force of the actuator cam for general die applications.

United States Patent Benedict 51 May 9,1972

1541 CAM FEEDER AND DIE [72] Inventor: Frank R. Benedict, Brightwaters,NY.

[73] Assignee: The Trane Company, La Crosse, Wis.

[22] Filed: Dec. 11, 1969 21 App1.No.: 884,238

[52] U.S. Cl ..72/421, 83/226 [51] Int. Cl. ...B21d 43/02, 826d 5/20[58] Field of Search ..72/42l,427, 361; 83/226;

[56] References Cited UNITED STATES PATENTS Richter ..72/36l Anderson..83/226 Anderson ..72/427 Primary E.\'aminerCharles W. Lanham AssistantExaminer-Robert M. Rogers Attorney-Irving Seidman [5 7 ABSTRACT In afeeder die system, a gag system is provided which is adapted tosimultaneously operate a plurality of actuators permitting reciptocatingmovement of feeder bar of a die. Provision is further made for utilizingthe actuating force of the actuator cam for general die applications.

4 Claims, 15 Drawing Figures PATENTEDHAY 9 mm SHEET 1 BF 6 t RJ I d 6Wm. WB WR k n m F ATTORNEY PATENTEDMAY 9|972 3,661,007

SHEET 2 BF 6 s4 82 no INVENTOR. Frank R. Benedict ATTORNEY PATENTEDMAY 9m2 3, 661 ,0 O7

SHEET 3 BF 6 INVENTOR Frank R.Bened|ct ATTORNEY PATENTEDMAY 9 I972 ShEET5 OF 6 INVENTOR. Frank R.Benedic1 ATTORNEY PATENTEDMAY 9 I972 SHEET 6 OF6 FIG.|4

INVENTOR. Frank R.Benedict FIG.|5

ATTORNEY CAM FEEDER AND DIE In the manufacture of uniformly dimensionedcollared openings, a thin sheet of metallic material is fed through apress equipped with a die for forming openings thereupon. The sheets ofmetal having such collared openings thereupon are subsequently slit toform fins for use in radiating surfaces in heat units, air conditioningequipment or the like. In feeding the sheet material through aprogressive die having a series of stations, an opening formed at afirst die station, and shaped at a second die station, provision must bemade for precisely advancing the material from die station to diestation between forming operations.

In US. Pat. No. 3,470,726, a long feed cam feeder with a skip move foruse in a feeder die system has been set forth in which the gag plateswere individually operated on each cam by separate air cylinders toproduce the skip move. As will be evident from the foregoing disclosure,synchronization of the cylinders is essential to produce gag or ungag onboth cams simultaneously. Although the operation of a system as thereindescribed is extremely efficient, the operation thereof at extremelyhigh speeds, as for example above 400 strokes per minute, indicated thepossibility of failure to attain exact synchronization of the cylindersto produce gag or ungag on both cams simultaneously would seriouslydamage the cam and/or feeder drive bar.

It is therefore an object of the present invention to provide in afeeder die system a single actuating system for introducing or removinggags upon more than one cam simultaneously.

Another object herein is to provide positive operation of more than onegag plate simultaneously so as to eliminate the possibility of having agag-in on one cam and a gag-out on a second cam.

Another object of this invention is the provision of a long feed camfeeder which is relatively quiet and shock free especially at highoperating speeds.

A further object of the present invention is the provision of a feederdie system having positive synchronization whereby a gag is either in orout on more than one cam.

In addition to utilization of the cams as parts of a feeder system, thecam feed system can be effectively employed for general dieapplications. Actuating force on a cam follower which usually carriesthe working tool, is derived from the ram and high forces are availableover a usually small follower travel. Total follower travel is limitedby the cam angle that may be used without friction lock-up. Utilizingthe long feed cam system with a full floating double cam combined with alow friction cam follower system provides large follower movementcoupled with high force transfer to the follower system. There are manydie applications where it is desirable to pass a large part directlythrough a die, performing work on the part as it is manually orautomatically indexed through the die. Quite often the work to be doneby the die is far inside the press, requiring long travel of the die tothe work area on the part coupled with the high die force at the workarea. The use of the long feed cams, as will be evident from theforegoing description, can effectively be employed as a die system.

Other important objects, advantages and features of the presentinvention will be apparent to those versed in the art from the followingdescription and accompanying drawings wherein like reference charactersdesignate like or corresponding parts in the several views and wherein:

FIG. 1 is a fragmentary side elevation of a cam feeder having some partsthereof shown in section;

FIG. 2 is a fragmentary side elevation of another cam feeder with someparts thereof shown in section;

FIG. 3 is a partial end view taken on line 3-3 of FIG. 2;

FIG. 4 is a fragmentary side elevation of the cam feeder shown in FIG. 2with the feeder bar actuator moved downwardly;

F IG. 5 is an end view of the cam feeder shown in FIG. 1;

FIG. 6 is a side elevation ofa feed finger;

FIG. 7 is a bottom view of the feed finger as shown in FIG.

FIG. 8 is a fragmentary side elevation of the cam feeder shown in FIGS.2 and 4 with the gag out;

FIG. 9 is a top plan view of the upper parts of the cam feeder with thetop die shown removed;

FIG. 10 is an elevational view of the cross rail shown in FIG. 9 andshowing the rocker arm in mid position;

FIG. 11 is an elevation of the cross rail shown in FIG. 10 showing therocker arm tipped for out-gag, moving the cross rail to the left againstthe stop block;

FIG. 12 is an elevation of the cross rail shown in FIG. 10 showing therocker arm tipped for in-gag, moving the cross rail to the right againstthe stop block;

FIG. 13 is a top plan view showing the positioning of the operatingblock and the gag-in and gag-out positions thereof;

FIG. 14 illustrates the use of the long feed cam as a die and showingthe die thereof in an open position; and

FIG. 15 is a view of the die as shown in FIG. 14, showing the die in aclosed position.

Referring now to the drawings, there is shown in FIG. 1 a die set 10adapted to be associated with a press (not shown). The die set 10generally includes a fixed lower die plate 12 mounted on the press toact as a platform for a feeder bar 14 which is endwise horizontallyreciprocable for moving the workpiece 15 in the desired direction oftravel, and an upper die plate 16 connected to the ram of a press bymeans of a bracing bar 17 to act as a support for a feeder bar actuator18 carried by the upper plate vertically toward and away from the lowerplate.

The vertical motion of actuator 18 is translated to horizontal feederbar motion through the combination of a cam face 20 formed in theforward surface 22 of actuator 18, and a cam follower 23 carried byfeeder bar, said cam follower being a roller 24 mounted on a shaft 26extending from the feeder bar across a slot 28 formed in the feeder barto receive actuator 18. As actuator 18 is moved into slot 28 cam face 20turns roller 24 on shaft 26 to move feeder bar 14 forward. Roller 24 isspring loaded toward the rear end against the forward surface 22 ofactuator 18 by a spring 30 which is compressed against a fixedly mountedstopping element 32 as the feeder bar is moved forwardly by theactuator. The rear end of the feeder bar is connected to the spring 30by way of a rod 34 extending from the feeder bar through an opening 36in element 32 and axially of the spring 30 to a spring adjustment collar38 which caps the end of spring remote from stop 32 and is threadablyconnected to rod 34. In operation, as the actuator 18 is moved upwardlyout of slot 28, the roller 24, now turning in the opposite direction onshaft 26, tracks cam face 20 as feeder bar is rearwardly returned byexpanding spring 30.

It will be obvious that with the foregoing arrangement the feeder barroller shaft 26 is subjected to the most stress when the angle of thecam face 20 subtends with respect to the depth of the actuator is least,the depth of the actuator being the maximum distance between therearward and forward surfaces 42, 22 of the actuator as measured along aline drawn parallel to the direction of the motion of the feeder bar. As

shown in FIG. 2, in order to reduce the mechanical stress on the feederbar roller shaft 26, the feeder bar actuator 18 is connected to theupper die plate 16 for horizontal reciprocation, forming an additionalcam face 40 on the rear surface 42 of actuator 18 and adding a camfollower 43 on the fixed lower die plate 12 with which the rearward camface 40 cooperates to horizontally reciprocate the actuator.

For the purpose of the following discussion it is assumed that the depthof the actuator has been predetermined. Ordinarily, the maximum depth ofthe actuator is limited by the length of stroke of the press to whichthe die set is adapted.

As best shown in FIGS. 2 and 3, the actuator 18 is reciprocably carriedbeneath the upper die plate 16 by means of a sliding bearing type ofinterconnection 50 between them, the fixed portion 52 of theinterconnection being associated with the upper die plate 16 and themovable portion 54 being associated with the actuator 18. The fixed andmovable portions 52, 54, respectively comprise an open-ended elongatedchannel member of inverted U-shaped cross-section connected to the upperdie plate to define a passageway 55 parallel to the direction of travelof the feeder bar, and an elongated slide bar connected to the upper endof the actuator 18. The slide bar 54 is endwise s'lidable in thepassageway 55 for carrying the actuator in the direction of travel ofthe feeder bar. A plurality of thrust rollers 56 located within thepassageway and in rolling contact with the upper surface of the slidebar 54 are mounted on shafts 57 extending across the passageway from theside walls of the channel 52. The lower end of the channel 52 is formedby a pair of elongated substantially parallel plates 58 extendinglaterally from the side walls of the channel to form an elongated loweropening 59 into the passageway 55. The plates 58 act as rails orguideways upon which the slide bar 54 is lengthwise seated. As the slidebar moves, its lower surface is held in sliding with the guide plates 58by the thrust rollers 56, the rollers turning in one direction or theother depending on the direction of motion of the slide bar. Since theactuator extends downwardly from the lower surface of the slide bar andthrough the passageway opening 59 it is guided for motion in thedirection of travel of the feeder bar by the plate 58.

The rear cam face 40 is formed in the rearward surface 42 of theactuator 18 to cooperate with the cam follower 43 associated with thefixed lower die plate 12. The cam follower 43 preferably comprises aroller 44 mounted on a shaft 46 extending from the fixed lower die plate12 across a slot 48 formed in the lower die plate 12 to receive theactuator 18. The lower die plate roller 44 is rotated in place on theshaft 46 by the actuator as it moves upwardly and downwardly in the slot48, the rearward cam face 40 coacting with the roller 44 to horizontallymove the actuator.

In operation, as the actuator moves downwardly into the lower die plateslot 48 the rearward cam face 40 turns the lower die plate roller 44 onits shaft 46 for forwardly moving the actuator 18. Since the actuator isin contact with the feeder bar roller 24, as the actuator movesforwardly the feeder bar is moved forwardly. FIG. 4 shows the actuator18 fully moved downwardly. As hereinbefore described in connection withFIG. 1, the feeder bar roller 24 is spring loaded towards the rearagainst the forward surface 22 of the actuator by the spring 30.Consequently, the rearward surface 42 of the actuator is urged towardsthe rear against the lower die plate roller 44. As the actuator movesupwardly out of the lower die plate slot 48, the feeder bar isrearwardly returned by the expanding spring 30. The rearwardly movingfeeder bar carries the actuator rearwardly. Thereupon the actuatorcauses the die plate roller 44 to turn in the opposite direction on itsshaft 46 and track the rearward cam face 40. While there operations arein progress the feeder bar causes the feeder bar roller 24 to track theforward cam face as hereinbefore described to further return the feederbar.

The arrangement allows the angle the forward cam face 20 subtends withrespect to the depth of the actuator to be increased to relieve stresson the feeder bar roller shaft 26, the feeder bar motion lost therebybeing made up for by the addition of the rearward cam face 40 and thestress being absorbed by the die plate roller shaft 46, Additionally, itshould be appreciated that the depth of the actuator may be increasedfor correspondingly increasing the distance the workpiece is advanced,and the forward and rearward cam faces of the actuator may be verticallyspaced apart from one another when they are formed in the actuatorsurfaces to move the feeder bar in two distinct sequential steps ratherthan in a single continuous step. The arrangement thus lends itself tomore complex forming operations at the option of the user.

With the improved arrangement, the feeder bar is fully advancedforwardly as the ram of the press moves downwardly and fully returnedrearwardly as the ram moves upwardly. As shown in FIG. 4, the forwardcam face 20 coacts with the forward cam follower 23 to advance thefeeder bar X" inches and the rearward cam face 40 coacts with therearward cam follower 43 to advance the feeder bar an additional Xinches; a total advancement of 2X inches during the downward stroke ofthe ram. The spring 30 described in connection with FIG, 1 returns thefeeder bar 2X inches during the upward stroke. As shown in FIGS. 1 and5, to transmit forward feeder bar motion to the workpiece 15, a materialcarrier 60 is connected to the forward end of the feeder bar forengaging the workpiece. The carrier 60 repeatedly engages the workpieceto advance the workpiece the same distance the feeder bar is forwardlymoved, and disengages the workpiece when the feeder bar is rearwardlymoved.

As best shown in FIG. 5 the carrier 60 basically includes an arm 62connected to the forward end of the feeder bar 14 such that the armoverhangs the workpiece 15. The overhanging portion of the arm 62 isequipped with a feed finger 66 which repeatedly engages the workpiece tomove the same when the feeder bar moves forwardly and repeatedlydisengages the workpiece when the feeder bar moves rearwardly.

In the embodiment shown in FIG. 5, the arm 62 is preferably pivoted tothe feeder bar by means of a pivot pin 63 having one end anchored to thearm 62 or the feeder bar 14, and the other end rotatably mounted in themember 62 or 14 to which it is not anchored. A spring 64 is mounted atthe feeder bar end 61 of the arm for urging the feed finger end of thearm towards the workpiece. As shown in FIGS. 5, 6 and 7, the feed finger66 preferably comprises an elongated body portion 67 terminated by ashaped lower end portion 69. The body portion 67 is resiliently mountedfor endwise motion in a bore 68 formed in the overhanging portion of thearm 62 from the side of the arm next adjacent the workpiece, and thelower end portion 69 is shaped to fit a part of the workpiece formed bythe die set; in this case, on opening formed in the workpiece at aprevious die station. In operation the lower end por' tion 69 repeatedlyengages the rim of opening to forwardly pull the workpiece when thefeeder bar moves forwardly, and repeatedly cams itself out of theopening thereby disengaging the workpiece when the feeder bar movesrearwardly. The feed finger 66 is contrained to prevent its rotation inplace by a pin 66A which laterally extends from the upper end portionand rides in a slot 62A formed in the arm 62. Further, a spring 12A, orplurality of springs 12A, may be mounted on the fixed lower die platebeneath the workpiece to urge the workpiece upwardly towards the feedfinger, insuring proper engagement and disengagement therebetween.

In another embodiment, the arm 62 may extend between the forward ends ofa pair of feeder bars sidewise spaced apart from one another andoperated in unison with one another by similarly spaced feeder baractuators. In this case it is desirable to fixedly mount the arm on theforward end of each of the feeder bars and eliminate the pivotarrangement hereinbefore described. As further described in the U.S.Pat. No. 3,470,726 and in U.S. Pat. No. 3,417,596, it may be desirableto add actuator extensions to the forward and/or rearward surfaces ofthe feeder bar actuator or shims intermediate the end of the feeder bar14 and the arm 62 to provide for a feed finger dropin distance of sayfifty thousandths of an inch, the drop-in distance being in excess ofthe distance the workpiece is moved. Still further, the depth of theforward cam face may be increased by use of shims to form a drop-indistance as an alternative to using shims at the end of the feeder bar.In any event, the feeder bar is not moved forwardly the drop-indistance. This distance is soly provided to allow the lower end portionof the feed finger to overrun the workpiece a distance slightly inexcess of 2X inches as the feeder bar actuator moves rearwardly so thatthe feed finger drops into the opening in the workpiece. In practice,the feeder bar is forwardly moved the drop-in distance before the lowerend portion of the feeder finger contacts the rim of the opening tocarry the workpiece forwardly. It is understood, of course, that theworkpiece is automatically formed by the dies after being moved, thedies being provided with means well known in the art for drawing and/orpiercing operations.

In any of the embodiments of the invention it may be desirable toprovide a material brake 70 at the rearward end of the die set as shownin FIG. 1 for exerting a holding force on the workpiece to partiallyresist the pulling force of the feeder bar finger 66, thus insuringaccurate displacement of the workpiece from die station to die station.The brake 70 comprises a lower member 72 fixedly mounted on the lowerdie plate 12 or a stationary part of the press, and an upper member 74movably connected to the lower member by a spring 75 and guide member 76arrangement which spring loads the upper member 74 downwardly towardsthe lower member 72. The guide member 76 is mounted on the lower member72 and extends upwardly from the lower member through an opening 78 inthe upper member 74 and then axially of the spring 75 to a springadjustment collar 79. The spring adjustment collar 79 caps the end ofthe spring remote from the collar 79 and is threadably connected to theguide member 76. Since the work-piece is fed between the lower and upperbrake members 72, 74, they respectively contact the lower and uppersurfaces of the workpiece and exert a holding force on the workpiecewhich may be increased or decreased by manipulating the brake adjustmentcollar 79.

In any of the embodiments herein described, or referred to, the lengthof stroke of a particular press may be somewhat reduced when a die setis adapted to the press since the die set may take up sufficient spacein the line of travel of the ram to forshorten the available length ofstroke. For example, in mounting the die set on a press the feeder barextends above a horizontal plan described by the uppermost surface ofthe lower die plate and is positioned below the ram of the press. If theportion of the press upon which the lower die plate is mounted cannot bedroped to allow the entire length of stroke of the ram to be utilized,the vertically extending dimension of the feeder bar will foreshortenthe length of stroke. In order to mount the feeder bar beneath the ramof the press without still further reducing the available length ofstroke as would occur if the plate 65 shown in FIGS. 1 and S wereutilized to incase the upper surface of the feeder bar, it is a featureherein to provide a feeder bar mounting arrangement which does notitself interfere with the length of stroke of the press. In any of theembodiments herein described it may thus be desirable to eliminate theencasement plate 65 and provide a pair of pillow blocks 31 in lieuthereof as shown in FIG. 4. The pillow blocks 31 are spaced apart fromone another and mounted on the lower die plate to support the ends ofthefeeder bar. In this arrangement the end portions 14A of the feeder barforwardly and rearwardly of the slot 28 are of reduced cross-section ascompared to the portion of the feeder bar in the vicinity of the slot,and each of the pillow blocks 31 is bored to receive one of the ends ofthe feeder bar to act as a guide therefor. With this arrangement thefeeder bar is both supported by the pillow blocks and is endwiseslidable therein. The pillow blocks may be provided with bearings 31A tominimize sliding friction without departing from the spirit and scope ofthe invention. It should be appreciated that the vertically extendingdimension of the pillow blocks may be made the same or less than that ofthe feeder bar to avoid foreshortening the available lengths of strokeof the ram. The material carrier, break and spring return means may beconnected as hereinbefore described, or referred to, to the end portions14A of the feeder bar.

In any of the embodiments herein described, or referred to, it is to benoted that the depth of the rearward cam face (X inches) may beincreased or decreased with respect to the depth of the forward cam face(X inches), without departing from the spirit and scope of theinvention. The distances are shown and described as being equal to oneanother to illustrate the inventive subject matter and not for thepurpose of limiting the same.

With the arrangements hereinbefore described a plurality of collaredopenings may for example be sequentially formed in sheet material atintervals between successive 2X inch advancements of the material toform radiating fins for home heating units. The collared openings may bespaced apart from one another either 2X inches or a fraction of the 2Xinch distance if more than one is to be formed simultaneously, but inany event the spaces between adjacent collared openings along thelongitudinal length of the material would be the same. A combination ofX and 2X inch advancements is not possible with the arrangementdescribed. However, it is another feature of the invention to allow forsuch a contingency by providing means for selectively arresting theforward and/or rearward motion of the actuator. It should be appreciatedthat if the actuator is immobilized the rearward cam face and lower dieplate roller will no longer coact with one another. Another feature ofthe invention is to provide a gag system which is adapted to operatemore than one die plate by a single actuator.

As illustrated in FIGS. 9 through 12, L-shaped gag plates are secured toa horizontally movable cross rail 82 which is carried across the upperdie plates 16. Cross rail 82 is caged in a cross rail cage 84 attachedto support blade 86. Stops 88 are secured to the upper die plates tolimit horizontal movement of cross rail 82 in either direction. In theout-gag position as illustrated in FIG. 1 1, the crossrail 82 isdisposed against the left stop 88, whereas in the in-gag position, thecross rail is against the right stop 89, total travel of said gag platesbeing the distance D.

An operating rocker arm assembly is pivotally mounted at each end ofcross rail 82 on supports 91, said supports secured to end stops 88, 89which in turn are attached to the upper die plate 16, said rocker armassembly 90 is comprised of a rocker arm 92 pivotally mounted on a hingepin 94 anchored to support block 91. A top roller 96 disposed within asubstantially U-shaped socket 83 in cross rail 82 is adapted tohorizontally move cross rail back and forth to produce the in-gag andout-gag condition of the system as heretofore indicated. A bottom in-gagroller 98 and bottom out-gag roller 99 mounted on rocker arm 92 isprovided for pivotal movement of the operating rocker arm assembly 90.Mounted upon the lower die plate 12, a guide rail 101 is provided,having affixed thereto an operating block carrier 102, and a pair ofmovable operating block cams 103, 104 alternatively adapted to movevertically.

The rocker arm assembly 90 is shown in FIG. 10 in mid position. Underthis condition gag plates 80 mounted in slots 85 would be positionedhalfway in, with respect to a gag position. The rocker arm 92 is tippedback and forth to produce gag functions by positioning the operatingblock cams 103, 104 under the appropriate roller 98 or 99 so as the diecloses and actuator 18 enters slot 48. The roller is moved upwardly totip rocker arm 92 and moves cross rail 82 to produce either gag-in orout.

FIG. 11 illustrates the tipping mode for gag-out. Operating blockcarrier 102 guided on rail 101 moves operating block cam 104 underroller 99 thus tipping rocker arm 92 counterclockwise causing roller 96to move cross rail 82 to the left against stop 88. Cross rail 82 isdetented at this position and will not be moved by rapid up and downmotion of the upper die plate 16. The detent comprises a conventionaldetent ball 110, a pressure pin, spring, and adjustable retaining screwlodged within a bore 1 l2, and is set at a position such that the detentforces itvto snap seat, the seating action itself moving the cross rail82 to produce a slight rocker arm tilt that lifts roller 99 aboveoperating block cam 104 so that roller 99 does not strike the cam onrepetitive die closures.

FIG. 12 illustrates the tipping mode for in-gag. Operating block carrier102 moves operating block cam 103 under roller 98, tipping the rockerarm 92 clockwise causing roller 96 to move the cross rail 82 to theright against stop block 88, at which point the gag plates 80 are fullyengaged with the end of slide bar 54 for in-gag.

Illustrated in FIG. 13 the positioning of operating block carrier 102 isshown. The block is guided by guide rail 101 and is moved between stops88 and 89, by means of air cylinder 106.

In a further embodiment of the present invention the cam follower whichusually carries the working tools is utilized to provide a die system.As illustrated in FIGS. 14 and 15 the actuator cam 18 and feeder bar 14are provided with a like, opposite set of members. Feeder bar 14 isprovided with one-half of a die 150 at the thereof. A similar die 151 inopposition thereto is positioned to allow a workpiece 15 to passthe'rebetween. Cam tail 152 on each of the cams are proportioned toprovide dwell time on the down stroke and up stroke of the ram 154 sothat the part to be processed may be moved simultaneously with rammovement through and positioned in the working opening for theworkpiece. As the ram descends the cam followers 23 and 43 are caused tomove away from the cams 18 carrying the die sections 150 and 151 ontheir ends toward each other as shown in FIG. 15. It is to be noted thatvertical motion of the ram is translated to horizontal motion in the,dies 150, 151. Although, the embodiment makes reference to two opposinghalf dies, one die as for example, memberl50 may be utilized to berammed against a solid block (not shown) against which a workpiece maybe disposed.

I claim:

1. In combination, a die set comprising:

a. a forming station including first die means mounted on a press;

b. complementary, reciprocating, movable die means mounted for movementtoward and away from said first die means;

pull-through feeder means for progressively advancing the material to beformed through said die set;

d. a reciprocating movable feeder bar mounted on said first die means;

e. means for advancing a workpiece in register with said feeder barduring each reciprocating cycle of said feeder bar;

f. feeder bar actuating means for moving said reciprocating movablefeeder bar;

g. reciprocating gag means including at least one gag plate secured to ahorizontally movable cross rail and cooperating with said feeder baractuating means to regulate the reciprocal travel of at least onemovable feeder bar;

travel of said cross rail during its horizontal forward and rearwardmovement;

d. rocker means mounted at each end of said cross rail for moving saidgag plates to an in-gag and alternatively an out-gag position.

3. The invention as defined in claim 2 wherein said stop means comprisea plurality of substantially L-shaped.blocks secured to the upper plateand defining the area of reciprocating travel of said cross rail.

4. The invention as defined in claim 2 wherein said rocker meanscomprise:

a. a support block secured to said stop means;

b. a rocker arm pivotally mounted to said support block;

c. said cross rail having a substantially U-shaped socket, and a toproller mounted in said socket, said roller adapted to horizontally movesaid cross rail forward and rearward to produce an in-gag and out-gagcondition;

d. a bottom in-gag roller and a bottom out-gag roller mounted on saidrocker arm adapted to provide a pivotal movement of said rocker arm;

e. a guide rail secured to said movable die means;

f. an operating block carrier mounted upon said guide rail; saidoperating block carrier being provided with a pair of vertically movableblock cams positioned within the body of said block adapted toalternately move the bottom ingag and bottom out-gag rollers so as tomove the cross rail forwardly and rearwardly and g. detent means forregulating vibratory movement of said cross rail.

1. In combination, a die set comprising: a. a forming station includingfirst die means mounted on a press; b. complementary, reciprocating,movable die means mounted for movement toward and away from said firstdie means; c. pull-through feeder means for progressively advancing thematerial to be formed through said die set; d. a reciprocating movablefeeder bar mounted on said first die means; e. means for aDvancing aworkpiece in register with said feeder bar during each reciprocatingcycle of said feeder bar; f. feeder bar actuating means for moving saidreciprocating movable feeder bar; g. reciprocating gag means includingat least one gag plate secured to a horizontally movable cross rail andcooperating with said feeder bar actuating means to regulate thereciprocal travel of at least one movable feeder bar; h. said dieshaving provision for forming the workpiece at the forming station duringeach cycle of the press.
 2. The invention as defined in claim 1 whereinsaid gag means comprise: a. a pair of substantially L-shaped gag plateseach secured to a corresponding end of said cross rail; b. a supportblock cage for securing said cross rail therein; c. stop means securedto the upper die plate for limiting travel of said cross rail during itshorizontal forward and rearward movement; d. rocker means mounted ateach end of said cross rail for moving said gag plates to an in-gag andalternatively an out-gag position.
 3. The invention as defined in claim2 wherein said stop means comprise a plurality of substantially L-shapedblocks secured to the upper plate and defining the area of reciprocatingtravel of said cross rail.
 4. The invention as defined in claim 2wherein said rocker means comprise: a. a support block secured to saidstop means; b. a rocker arm pivotally mounted to said support block; c.said cross rail having a substantially U-shaped socket, and a top rollermounted in said socket, said roller adapted to horizontally move saidcross rail forward and rearward to produce an in-gag and out-gagcondition; d. a bottom in-gag roller and a bottom out-gag roller mountedon said rocker arm adapted to provide a pivotal movement of said rockerarm; e. a guide rail secured to said movable die means; f. an operatingblock carrier mounted upon said guide rail; said operating block carrierbeing provided with a pair of vertically movable block cams positionedwithin the body of said block adapted to alternately move the bottomin-gag and bottom out-gag rollers so as to move the cross rail forwardlyand rearwardly, and g. detent means for regulating vibratory movement ofsaid cross rail.